JP2019038352A - Air conditioner for vehicle - Google Patents

Abstract

An air conditioner for a vehicle is provided that can eliminate the inconvenience due to a decrease in heating capacity when switching from heat absorption from outside air to heat absorption from a heat medium. An exothermic device temperature adjusting device includes a heat medium heater and a refrigerant-heat medium heat exchanger. The refrigerant discharged from the compressor 2 is dissipated by the radiator 4, and after the decompressed refrigerant is depressurized, first and second heat medium heat absorption / heating modes for absorbing heat by the refrigerant-heat medium heat exchanger are provided. When switching from the heating operation to the first and second heat medium absorption / heating modes, if the temperature of the heat medium is equal to or lower than a predetermined threshold T1, the heat medium is heated by the heat medium heater before switching. [Selection] Figure 1

Description

  The present invention relates to a heat pump type air conditioner that air-conditions a vehicle interior of a vehicle, and more particularly to a vehicle air conditioner suitable for a hybrid vehicle or an electric vehicle equipped with a heat generating device such as a battery.

  With the recent emergence of environmental problems, hybrid vehicles and electric vehicles that drive electric motors for traveling with electric power supplied from batteries have become widespread. As an air conditioner that can be applied to such a vehicle, a compressor that compresses and discharges the refrigerant, a radiator that is provided on the vehicle interior side and dissipates the refrigerant, and is provided on the vehicle interior side. A heat sink that absorbs the refrigerant and a refrigerant circuit that is provided outside the passenger compartment and vents the outside air and that is connected to an outdoor heat exchanger that absorbs or dissipates the refrigerant, and dissipates the refrigerant discharged from the compressor. A heating mode (heating operation) in which heat is radiated in the radiator, and the refrigerant radiated in the radiator is absorbed in the outdoor heat exchanger, and cooling in which the refrigerant discharged from the compressor is radiated in the outdoor heat exchanger and absorbed in the heat absorber One that switches and executes a mode (cooling operation) has been developed (see, for example, Patent Document 1).

  On the other hand, for example, a battery (heat generating device) mounted on the vehicle becomes high temperature due to self-heating during charging or discharging. When charging / discharging is performed in such a state, the deterioration proceeds, and there is a risk of eventually causing malfunction and damage. Then, what can adjust the temperature of a secondary battery (battery) by circulating the air (heat medium) cooled with the refrigerant | coolant which circulates through a refrigerant circuit to a battery is also developed (for example, Patent Document 2).

JP 2014-213765 A JP-A-2006-90201

  Here, by allowing the refrigerant to absorb heat from the heat medium so that the heat of the heat generating device such as a battery can be used for heating the vehicle interior, the progress of frost formation on the outdoor heat exchanger can be delayed. In addition, when the outdoor heat exchanger is frosted and cannot absorb heat from the outside air, it is possible to heat the vehicle interior by absorbing heat from the heat medium.

  However, when the outdoor heat exchanger switches from an operation state in which heat is absorbed from outside air to an operation state in which heat is absorbed from the heat medium, if the temperature of the heat medium is cold, the heating capacity is significantly reduced and blown into the vehicle interior. There is a problem that the temperature of the air is temporarily lowered, which causes the passenger to feel uncomfortable or uncomfortable.

  The present invention has been made to solve the conventional technical problems, and is for a vehicle that can eliminate the disadvantage caused by a decrease in heating capacity when switching from heat absorption from outside air to heat absorption from a heat medium. An object is to provide an air conditioner.

  The vehicle air conditioner of the present invention heats the compressor that compresses the refrigerant, the air flow passage through which the air supplied to the vehicle interior flows, and the air that dissipates the refrigerant and is supplied from the air flow passage to the vehicle interior. A heat radiator, an outdoor heat exchanger that is provided outside the passenger compartment to absorb the refrigerant, and a control device, and at least the refrigerant discharged from the compressor is radiated by the heat radiator by the control device, After reducing the pressure of the radiated refrigerant, a heating operation is performed in which heat is absorbed by the outdoor heat exchanger, and the heat medium is circulated through the heat generating device mounted on the vehicle to adjust the temperature of the heat generating device. The heat generating device temperature adjusting device has a heating device for heating the heat medium, and a refrigerant-heat medium heat exchanger for heat exchange between the refrigerant and the heat medium, The control device discharges from the compressor The heat-dissipating refrigerant is radiated by a radiator, and the radiated refrigerant is decompressed, and then has a heat-medium heat absorption / heating mode in which heat is absorbed by a refrigerant-heat medium heat exchanger. When the temperature of the heat medium is equal to or lower than the predetermined threshold T1, the heat medium is heated by the heating device and the temperature of the heat medium is increased before switching to the heat medium heat absorption / heating mode. It is characterized by switching to the medium endothermic / heating mode.

  According to a second aspect of the present invention, there is a possibility that the control device may not be able to absorb heat from the outside air in the outdoor heat exchanger when the predetermined outside air heat absorption impossibility prediction determination condition is satisfied in the heating operation. It is determined whether or not the temperature of the heat medium is equal to or lower than the threshold value T1, and if it is equal to or lower than the threshold value T1, heating of the heat medium by the heating device is started, and the temperature of the heat medium is at least higher than the threshold value T1 It waits for it to rise, and it transfers to heat-medium heat absorption / heating mode, It is characterized by the above-mentioned.

  In the air conditioning apparatus for a vehicle according to the third aspect of the present invention, in the above-described invention, the outside air heat absorption impossibility prediction determination condition is that the suction refrigerant temperature Ts of the compressor has decreased to a predetermined value Ts1 or less, and the amount of frost on the outdoor heat exchanger. Has increased to a predetermined value Fr1 or more, the frosting speed to the outdoor heat exchanger has increased to a predetermined value X1 or more, the outside air temperature Tam has decreased to a predetermined value Tam1 or less, and the outside air temperature Tam decreasing rate Including at least one of the above-described rises to a predetermined value Y1 or more.

  According to a fourth aspect of the present invention, there is provided an air conditioning apparatus for a vehicle according to the present invention, wherein the control device includes a target heating capacity TGQhp of the radiator, a target blowing temperature TAO that is a target value of the air temperature blown into the passenger compartment, The threshold value T1 is determined based on at least one of the voltage BLV of the indoor blower that is ventilated in the air and the target heater temperature TCO that is the target value of the temperature of the leeward air of the radiator.

  According to a fifth aspect of the present invention, there is provided an air conditioning apparatus for a vehicle according to each of the first and second aspects of the present invention, wherein when the control device executes the heat medium heat absorption / heating mode, if the predetermined outdoor air heat absorption capability determination condition is satisfied, It is determined that heat can be absorbed from the refrigerant, and the refrigerant radiated by the radiator is absorbed by the outdoor heat exchanger and the refrigerant-heat medium heat exchanger.

  In the vehicle air conditioner according to the sixth aspect of the present invention, in the above invention, the outdoor air heat absorption possibility determination condition is that the suction refrigerant temperature Ts of the compressor is equal to or higher than a predetermined value Ts2 lower than the predetermined value Ts1, and the outdoor heat exchanger The amount of frost formation is equal to or less than a predetermined value Fr2 greater than the predetermined value Fr1, the progress speed of frost formation to the outdoor heat exchanger is equal to or less than a predetermined value X2, which is earlier than the predetermined value X1, and the outside air temperature Tam is higher than the predetermined value Tam1. It includes at least one of a low predetermined value Tam2 or higher and a lowering speed of the outside air temperature Tam that is lower than a predetermined value Y2 higher than the predetermined value Y1.

  According to the present invention, a compressor for compressing a refrigerant, an air flow passage through which air to be supplied to the vehicle interior flows, and a radiator for heating the air to be radiated from the refrigerant and supplied to the vehicle interior from the air flow passage. And an outdoor heat exchanger that is provided outside the passenger compartment to absorb the refrigerant, and a control device, and at least the refrigerant discharged from the compressor is radiated by the radiator by the control device, and the radiated refrigerant In a vehicle air conditioner that performs a heating operation in which heat is absorbed by an outdoor heat exchanger after the pressure is reduced, heat generated by adjusting the temperature of the heat generating device by circulating a heat medium to the heat generating device mounted on the vehicle The apparatus includes a device temperature adjusting device, the heat generating device temperature adjusting device includes a heating device for heating the heat medium, and a refrigerant-heat medium heat exchanger for heat exchange between the refrigerant and the heat medium, and a control device. Is discharged from the compressor Since it has a heat-medium heat absorption / heating mode in which the radiated refrigerant is dissipated by a radiator and the radiated refrigerant is depressurized and then absorbed by a refrigerant-heat medium heat exchanger, switch to this heat medium heat absorption / heating mode. If so, heat is absorbed from the heat medium of the heat generating device temperature control device to efficiently heat the vehicle interior, for example, appropriately cooling the heat generating device while suppressing frost formation on the outdoor heat exchanger, or Even when the heat exchanger frosts and cannot absorb heat from the outside air, the vehicle interior can be heated by absorbing heat from the heat medium of the heat generating device temperature adjusting device.

  In particular, when the control device switches from the heating operation to the heat medium heat absorption / heating mode, if the temperature of the heat medium is equal to or lower than a predetermined threshold T1, the control device uses the heating device to change the heat medium before switching to the heat medium heat absorption / heating mode. After heating and raising the temperature of the heat medium, the heat medium heat absorption / heating mode is switched, so that sufficient heating capacity can be ensured when switching from the heating operation to the heat medium heat absorption / heating mode. Become. As a result, the heat medium heat absorption / heating mode is switched to a state where the temperature of the heat medium is low, and the inconvenience that the passenger feels uncomfortable or uncomfortable due to a temporary decrease in the blowing temperature can be solved.

  Further, as in the second aspect of the invention, the control device determines that the outdoor heat exchanger may not be able to absorb heat from the outside air when the predetermined outside air heat absorption impossibility prediction determination condition is satisfied in the heating operation, and the temperature of the heat medium Is less than or equal to the threshold value T1, and if it is equal to or less than the threshold value T1, heating of the heat medium by the heating device is started, and waits for the temperature of the heat medium to rise to at least a temperature higher than the threshold value T1. By shifting to the heat medium heat absorption / heating mode, the switching from the heating operation to the heat medium heat absorption / heating mode can be performed smoothly.

  In this case, the outdoor air heat absorption impossibility prediction determination condition is that, as in the third aspect of the invention, the suction refrigerant temperature Ts of the compressor is lowered to a predetermined value Ts1 or less, and the amount of frost formation on the outdoor heat exchanger is predetermined. Increase in value Fr1 or higher, progress rate of frost formation on outdoor heat exchanger increased to a predetermined value X1 or higher, outdoor air temperature Tam decreased to a predetermined value Tam1 or lower, outdoor air temperature Tam decrease rate predetermined It is preferable to include at least one of the rises to the value Y1 or more.

  Further, as in the fourth aspect of the present invention, the control device includes the target heating capacity TGQhp of the radiator, the target blowing temperature TAO which is a target value of the air temperature blown into the vehicle interior, and the voltage BLV of the indoor blower passing through the air flow passage. If the threshold value T1 is determined based on at least one of the target heater temperature TCO that is the target value of the air temperature on the lee side of the radiator, the heating medium needs to be heated by the heating device. It is possible to appropriately determine whether or not heating by an unnecessary heating device can be avoided.

  Further, when the control device executes the heat medium heat absorption / heating mode as in the fifth aspect of the invention, it is determined that the outdoor heat exchanger can absorb heat from the outside air when a predetermined outside air heat absorption possibility determination condition is satisfied. If the heat dissipated by the radiator is absorbed by the outdoor heat exchanger and the refrigerant-heat medium heat exchanger, if the outdoor heat exchanger can absorb heat from the outside air, the heat absorption from the heat medium At the same time, it also absorbs heat from outside air and can heat the passenger compartment.

  In this case, the outdoor air heat absorption possibility determination condition is that, as in the sixth aspect of the invention, the suction refrigerant temperature Ts of the compressor is equal to or higher than a predetermined value Ts2 lower than the predetermined value Ts1, and frost formation on the outdoor heat exchanger is performed. The amount is not more than a predetermined value Fr2 greater than the predetermined value Fr1, the frosting speed to the outdoor heat exchanger is not more than a predetermined value X2, which is faster than the predetermined value X1, and the outside air temperature Tam is lower than the predetermined value Tam1. It is preferable that it is at least one of being not less than the value Tam2 and not more than a predetermined value Y2 at which the rate of decrease in the outside air temperature Tam is lower than the predetermined value Y1.

It is a block diagram of the air conditioning apparatus for vehicles of one Embodiment to which this invention is applied. It is a block diagram of the electric circuit of the controller of the vehicle air conditioner of FIG. It is a figure explaining the heating operation by the controller of FIG. It is a figure explaining the dehumidification heating operation by the controller of FIG. It is a figure explaining the internal cycle driving | operation by the controller of FIG. It is a figure explaining the dehumidification cooling operation by the controller of FIG. It is a figure explaining the cooling operation by the controller of FIG. It is a figure explaining the 1st heat carrier heat absorption / heating mode by the controller of FIG. It is a figure explaining the 2nd heat carrier heat absorption / heating mode by the controller of FIG. 3 is a flowchart for explaining switching control from a heating operation to a first heat medium heat absorption / heating mode and a second heat medium heat absorption / heating mode by the controller of FIG. 2 when there is a possibility that the outside air cannot absorb heat. FIG. 3 is a diagram for explaining a heat medium temperature MAP that can be transferred to the heat medium endotherm included in the controller of FIG. 2. It is a figure explaining the temperature change of each part at the time of switching from heating operation to 2nd heat-medium heat absorption / heating mode although there exists a possibility that external air heat absorption is impossible. It is a ph diagram of a refrigerant circuit in case heat medium preheating operation is carried out. It is a ph diagram of a refrigerant circuit when not carrying out heat carrier preheating operation.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

  FIG. 1 shows a configuration diagram of a vehicle air conditioner 1 according to an embodiment of the present invention. A vehicle according to an embodiment to which the present invention is applied is an electric vehicle (EV) in which an engine (internal combustion engine) is not mounted. The battery 55 is mounted on the vehicle, and electric power charged in the battery 55 is used for traveling. The vehicle air conditioner 1 according to the present invention is driven by the electric power of the battery 55. The vehicle air conditioner 1 of the present invention is also driven by being supplied to an electric motor (not shown).

  That is, the vehicle air conditioner 1 of the embodiment performs heating operation by heat pump operation using the refrigerant circuit R in an electric vehicle that cannot be heated by engine waste heat, and further performs dehumidification heating operation, internal cycle operation, and dehumidification cooling. Air conditioning of the passenger compartment is performed by selectively executing each air conditioning operation of the operation and the cooling operation.

  Note that the present invention is not limited to an electric vehicle as a vehicle, but is also applicable to a so-called hybrid vehicle that uses an engine and an electric motor for traveling, and is also applicable to a normal vehicle that travels with an engine. Needless to say.

  The vehicle air conditioner 1 according to the embodiment performs air conditioning (heating, cooling, dehumidification, and ventilation) in a vehicle interior of an electric vehicle, and includes an electric compressor 2 that compresses refrigerant and vehicle interior air. Is provided in the air flow passage 3 of the HVAC unit 10 through which air is circulated, and the high-temperature and high-pressure refrigerant discharged from the compressor 2 flows in through the refrigerant pipe 13G, and dissipates the refrigerant into the vehicle compartment. And an outdoor expansion valve 6 comprising an electric valve that decompresses and expands the refrigerant during heating, and functions as a radiator that radiates the refrigerant during cooling and functions as an evaporator that absorbs the refrigerant during heating. An outdoor heat exchanger 7 that performs heat exchange, an indoor expansion valve 8 that includes an electric valve (or a mechanical expansion valve) that decompresses and expands the refrigerant, and a vehicle that is provided in the air flow passage 3 during cooling and dehumidification Absorbs heat from inside and outside into refrigerant A heat absorber 9 to the accumulator 12 and the like are sequentially connected by a refrigerant pipe 13, the refrigerant circuit R is formed. The outdoor expansion valve 6 expands the refrigerant flowing out of the radiator 4 and flowing into the outdoor heat exchanger 7 under reduced pressure, and can be fully closed.

  The outdoor heat exchanger 7 is provided with an outdoor blower 15. The outdoor blower 15 exchanges heat between the outside air and the refrigerant by forcibly passing outside air through the outdoor heat exchanger 7, so that the outdoor air blower 15 can also be used outdoors even when the vehicle is stopped (that is, the vehicle speed is 0 km / h). It is comprised so that external air may be ventilated by the heat exchanger 7. FIG. In the figure, reference numeral 23 denotes a shutter called a grill shutter. When the shutter 23 is closed, the traveling wind is prevented from flowing into the outdoor heat exchanger 7.

  The refrigerant pipe 13 </ b> A connected to the refrigerant outlet side of the outdoor heat exchanger 7 is connected to the refrigerant pipe 13 </ b> B via the check valve 18. The check valve 18 has a forward direction on the refrigerant pipe 13B side. The refrigerant pipe 13B is connected to the indoor expansion valve 8 via an electromagnetic valve 17 serving as an on-off valve that is opened during cooling. In the embodiment, the electromagnetic valve 17 and the indoor expansion valve 8 constitute a valve device for controlling the inflow of the refrigerant to the heat absorber 9.

  Further, the refrigerant pipe 13A exiting from the outdoor heat exchanger 7 is branched, and this branched refrigerant pipe 13D is a refrigerant pipe 13C located on the outlet side of the heat absorber 9 via an electromagnetic valve 21 opened during heating. It is connected in communication. Then, the refrigerant pipe 13C after the refrigerant pipe 13D has joined is connected to the accumulator 12 via the check valve 40, and the accumulator 12 is connected to the refrigerant suction side of the compressor 2. The check valve 40 has a forward direction on the accumulator 12 side.

  Furthermore, the refrigerant pipe 13E on the outlet side of the radiator 4 is branched into a refrigerant pipe 13J and a refrigerant pipe 13F before the outdoor expansion valve 6 (the refrigerant upstream side), and one of the branched refrigerant pipes 13J is the outdoor expansion valve 6. Is connected to the refrigerant inlet side of the outdoor heat exchanger 7. Also, the other branched refrigerant pipe 13F is a refrigerant pipe 13A and a refrigerant pipe 13B located on the refrigerant downstream side of the check valve 18 and on the refrigerant upstream side of the electromagnetic valve 17 via the electromagnetic valve 22 opened at the time of dehumidification. It is connected to the connection part.

  Thus, the refrigerant pipe 13F is connected in parallel to the series circuit of the outdoor expansion valve 6, the outdoor heat exchanger 7 and the check valve 18, and the outdoor expansion valve 6, the outdoor heat exchanger 7 and the check valve are connected. The circuit bypasses the circuit 18. An electromagnetic valve 20 is connected in parallel to the outdoor expansion valve 6.

  The air flow passage 3 on the air upstream side of the heat absorber 9 is formed with each of an outside air inlet and an inside air inlet (represented by the inlet 25 in FIG. 1). 25 is provided with a suction switching damper 26 for switching the air introduced into the air flow passage 3 between the inside air (inside air circulation) which is air inside the vehicle compartment and the outside air (outside air introduction) which is outside the vehicle compartment. Furthermore, an indoor blower (blower fan) 27 for supplying the introduced inside air or outside air to the air flow passage 3 is provided on the air downstream side of the suction switching damper 26.

  Further, the air (inside air and outside air) in the air flow passage 3 after flowing into the air flow passage 3 and passing through the heat absorber 9 is radiated into the air flow passage 3 on the air upstream side of the radiator 4. An air mix damper 28 that adjusts the rate of ventilation through the vessel 4 is provided. Further, FOOT (foot), VENT (vent), and DEF (def) outlets (represented by the outlet 29 as a representative in FIG. 1) are formed in the air flow passage 3 on the air downstream side of the radiator 4. The air outlet 29 is provided with an air outlet switching damper 31 that performs switching control of air blowing from the air outlets.

  Furthermore, the vehicle air conditioner 1 of the present invention includes a heat generating device temperature adjustment device 61 for adjusting the temperature of the battery 55 by circulating a heat medium through the battery 55. In the embodiment, the battery 55 is taken as an example of the heat generating device in the present invention. However, the heat generating device is not limited thereto, and may be an electric motor for traveling, an inverter for controlling the motor, or the like.

  The heat generating device temperature adjusting device 61 of this embodiment includes a circulation pump 62 as a circulation device for circulating a heat medium to the battery 55 (heat generating device), a heat medium heater 66 as a heating device, and a refrigerant-heat medium. A heat exchanger 64 is provided, and the battery 55 and the battery 55 are annularly connected by a heat medium pipe 68.

  In the case of the embodiment, the heat medium heater 66 is connected to the discharge side of the circulation pump 62, and the inlet of the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64 is connected to the outlet of the heat medium heater 66. The inlet of the battery 55 is connected to the outlet of the heat medium flow path 64 </ b> A, and the outlet of the battery 55 is connected to the suction side of the circulation pump 62.

  As the heat medium used in the heat generating device temperature adjusting device 61, for example, water, a refrigerant such as HFO-1234f, a liquid such as a coolant, or a gas such as air can be employed. In the embodiment, water is used as the heat medium. The heat medium heater 66 is composed of an electric heater such as a PTC heater. Furthermore, it is assumed that a jacket structure is provided around the battery 55 so that the heat medium can circulate with the battery 55 in a heat exchange relationship.

  When the circulation pump 62 is operated, the heat medium discharged from the circulation pump 62 reaches the heat medium heater 66. If the heat medium heater 66 generates heat, it is heated there, and then It flows into the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64. The heat medium exiting the heat medium flow path 64 </ b> A of the refrigerant-heat medium heat exchanger 64 reaches the battery 55. The heat medium exchanges heat therewith with the battery 55 and is then circulated through the heat medium pipe 68 by being sucked into the circulation pump 62.

  On the other hand, the outlet of the refrigerant pipe 13F of the refrigerant circuit R, that is, the connecting portion between the refrigerant pipe 13F, the refrigerant pipe 13A, and the refrigerant pipe 13B is on the refrigerant downstream side (forward direction side) of the check valve 18 and is electromagnetically One end of a branch pipe 72 serving as a branch circuit is connected to the upstream side of the refrigerant of the valve 17. The branch pipe 72 is provided with an auxiliary expansion valve 73 composed of an electric valve. The auxiliary expansion valve 73 decompresses and expands the refrigerant flowing into a refrigerant flow path 64B (described later) of the refrigerant-heat medium heat exchanger 64 and can be fully closed. The other end of the branch pipe 72 is connected to the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64, and one end of the refrigerant pipe 74 is connected to the outlet of the refrigerant flow path 64B. The other end is connected to the refrigerant pipe 13 </ b> C in front of the accumulator 12 (on the refrigerant upstream side of the accumulator 12 and on the refrigerant downstream side of the check valve 40). The auxiliary expansion valve 73 and the like constitute a part of the refrigerant circuit R, and at the same time, a part of the heat generating device temperature adjusting device 61.

  When the auxiliary expansion valve 73 is open, the refrigerant (a part or all of the refrigerant) discharged from the refrigerant pipe 13F and the outdoor heat exchanger 7 is decompressed by the auxiliary expansion valve 73, and then the refrigerant-heat medium heat exchanger. 64 flows into the refrigerant flow path 64B and evaporates there. The refrigerant absorbs heat from the heat medium flowing through the heat medium flow path 64A in the process of flowing through the refrigerant flow path 64B, and then is sucked into the compressor 2 through the accumulator 12.

Next, in FIG. 2, 32 is a controller (ECU) as a control device. The controller 32 includes a microcomputer as an example of a computer having a processor, and inputs include an outside air temperature sensor 33 that detects the outside air temperature (Tam) of the vehicle and an outside air humidity sensor that detects the outside air humidity. 34, an HVAC suction temperature sensor 36 for detecting the temperature of the air sucked into the air flow passage 3 from the suction port 25, an inside air temperature sensor 37 for detecting the temperature of the air (inside air) in the passenger compartment, and the air in the passenger compartment An inside air humidity sensor 38 that detects humidity, an indoor CO ₂ concentration sensor 39 that detects carbon dioxide concentration in the vehicle interior, a blowout temperature sensor 41 that detects the temperature of air blown from the blowout port 29 into the vehicle interior, and a compression A discharge pressure sensor 42 for detecting the discharge refrigerant pressure (discharge pressure Pd) of the compressor 2 and a discharge temperature sensor for detecting the discharge refrigerant temperature of the compressor 2 3, a suction temperature sensor 44 that detects the suction refrigerant temperature Ts of the compressor 2, and a heat release that detects the temperature of the radiator 4 (in the embodiment, the temperature of the refrigerant immediately after leaving the radiator 4: the radiator temperature TCI). A radiator temperature sensor 46, a radiator pressure sensor 47 for detecting the refrigerant pressure of the radiator 4 (the pressure of the refrigerant in the radiator 4 or immediately after leaving the radiator 4: the radiator pressure PCI), and the heat absorber 9. And a refrigerant pressure of the heat absorber 9 (in the heat absorber 9, or the temperature of the air passing through the heat absorber 9 or the temperature of the heat absorber 9 itself: the heat absorber temperature Te) A heat absorber pressure sensor 49 for detecting the pressure of the refrigerant immediately after exiting the heat absorber 9, a photosensor-type solar sensor 51 for detecting the amount of solar radiation into the passenger compartment, and the moving speed (vehicle speed) of the vehicle. A vehicle speed sensor 52 for detecting the Air conditioning (air conditioner) operation unit 53 for setting switching and the temperature of the outdoor heat exchanger 7 (the temperature of the refrigerant immediately after coming out of the outdoor heat exchanger 7 or the temperature of the outdoor heat exchanger 7 itself: outdoor heat An exchanger temperature TXO, when the outdoor heat exchanger 7 functions as an evaporator, the outdoor heat exchanger temperature TXO detects the refrigerant evaporation temperature in the outdoor heat exchanger 7), Refrigerant pressure of the outdoor heat exchanger 7 (pressure of the refrigerant in the outdoor heat exchanger 7 or immediately after exiting the outdoor heat exchanger 7: outdoor heat exchanger pressure PXO. Evaporation pressure of refrigerant in the outdoor heat exchanger 7 and Each output of the outdoor heat exchanger pressure sensor 56 is detected.

  Further, the input of the controller 32 further includes a battery temperature sensor that detects the temperature of the battery 55 (the temperature of the battery 55 itself, the temperature of the heat medium that has exited the battery 55, or the temperature of the heat medium that enters the battery 55). 76, a heat medium heater temperature sensor 77 that detects the temperature of the heat medium heater 66 (the temperature of the heat medium heater 66 itself), and the temperature of the heat medium that has exited the heat medium heater 66 (heat medium temperature Tw). The heat medium temperature sensor 80 to detect, the 1st exit temperature sensor 78 which detects the temperature of the heat medium which exited the heat medium flow path 64A of the refrigerant | coolant-heat medium heat exchanger 64, and the refrigerant | coolant which left the refrigerant flow path 64B Each output of the 2nd exit temperature sensor 79 which detects temperature is also connected.

  On the other hand, the output of the controller 32 includes the compressor 2, the outdoor blower 15, the indoor blower (blower fan) 27, the suction switching damper 26, the air mix damper 28, the outlet switching damper 31, and the outdoor expansion. Valve 6, indoor expansion valve 8, solenoid valve 22 (dehumidification), solenoid valve 17 (cooling), solenoid valve 21 (heating), solenoid valve 20 (bypass) solenoid valve, shutter 23, circulation pump 62, heat A medium heater 66 and an auxiliary expansion valve 73 are connected. And the controller 32 controls these based on the output of each sensor and the setting input in the air-conditioning operation part 53. FIG.

  Next, the operation of the vehicle air conditioner 1 having the above-described configuration will be described. In the embodiment, the controller 32 switches between the air-conditioning operation of the heating operation, the dehumidifying heating operation, the internal cycle operation, the dehumidifying and cooling operation, and the cooling operation, and adjusts the temperature of the battery 55 within a predetermined appropriate temperature range. To do. First, each air conditioning operation of the refrigerant circuit R will be described.

(1) Heating Operation First, the heating operation will be described with reference to FIG. FIG. 3 shows a refrigerant flow (solid arrow) in the refrigerant circuit R in the heating operation. When the heating operation is selected by the controller 32 (auto mode) or by the manual operation (manual mode) to the air conditioning operation unit 53, the controller 32 opens the electromagnetic valve 21 (for heating) and the electromagnetic valve 17 (cooling). Close). Further, the solenoid valve 22 (for dehumidification) and the solenoid valve 20 (for bypass) are closed. The shutter 23 is opened.

  And the compressor 2 and each air blower 15 and 27 are drive | operated, and the air mix damper 28 sets it as the state which adjusts the ratio by which the air blown out from the indoor air blower 27 is ventilated by the heat radiator 4. FIG. Thereby, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4. Since the air in the air flow passage 3 is passed through the radiator 4, the air in the air flow passage 3 is heated by the high-temperature refrigerant in the radiator 4, while the refrigerant in the radiator 4 heats the air. Deprived, cooled, and condensed into liquid.

  The refrigerant liquefied in the radiator 4 exits the radiator 4 and then reaches the outdoor expansion valve 6 through the refrigerant pipes 13E and 13J. The refrigerant flowing into the outdoor expansion valve 6 is decompressed there and then flows into the outdoor heat exchanger 7. The refrigerant flowing into the outdoor heat exchanger 7 evaporates, and pumps up heat from the outside air that is ventilated by traveling or by the outdoor blower 15 (heat absorption). That is, the refrigerant circuit R becomes a heat pump. Then, the low-temperature refrigerant that has exited the outdoor heat exchanger 7 enters the accumulator 12 from the refrigerant pipe 13C through the refrigerant pipe 13A, the refrigerant pipe 13D, the electromagnetic valve 21, and the check valve 40 in this order, and is separated into gas and liquid there. The circulation in which the gas refrigerant is sucked into the compressor 2 is repeated. Since the air heated by the radiator 4 is blown out from the air outlet 29, the vehicle interior is thereby heated.

  The controller 32 calculates a target radiator pressure PCO (heat radiator 4 from a target heater temperature TCO (a target value of a heating temperature TH described later, which is a temperature of air on the leeward side of the radiator 4) calculated from a target outlet temperature TAO described later. The target pressure PCI) is calculated and compressed based on the target radiator pressure PCO and the refrigerant pressure of the radiator 4 detected by the radiator pressure sensor 47 (radiator pressure PCI; high pressure of the refrigerant circuit R). The rotational speed of the machine 2 is controlled, and the outdoor expansion valve 6 is controlled based on the temperature of the radiator 4 (the radiator temperature TCI) detected by the radiator temperature sensor 46 and the radiator pressure PCI detected by the radiator pressure sensor 47. The valve opening degree is controlled, and the degree of supercooling of the refrigerant at the outlet of the radiator 4 is controlled. The target heater temperature TCO is basically set to TCO = TAO, but a predetermined restriction on control is provided.

(2) Dehumidifying and Heating Operation Next, the dehumidifying and heating operation will be described with reference to FIG. FIG. 4 shows the refrigerant flow (solid arrow) in the refrigerant circuit R in the dehumidifying heating operation. In the dehumidifying heating operation, the controller 32 opens the electromagnetic valve 22 and the electromagnetic valve 17 in the heating operation state. Further, the shutter 23 is opened. Thereby, a part of the condensed refrigerant flowing through the refrigerant pipe 13E through the radiator 4 is divided, and the divided refrigerant flows into the refrigerant pipe 13F through the electromagnetic valve 22, and flows from the refrigerant pipe 13B to the indoor expansion valve 8. The remaining refrigerant flows into the outdoor expansion valve 6. That is, a part of the divided refrigerant is decompressed by the indoor expansion valve 8 and then flows into the heat absorber 9 to evaporate.

  The controller 32 controls the opening degree of the indoor expansion valve 8 so that the degree of superheat (SH) of the refrigerant at the outlet of the heat absorber 9 is maintained at a predetermined value. Since moisture in the air blown out from the indoor blower 27 condenses and adheres to the heat absorber 9, the air is cooled and dehumidified. The remaining refrigerant that is divided and flows into the refrigerant pipe 13J is depressurized by the outdoor expansion valve 6 and then evaporated by the outdoor heat exchanger 7.

  The refrigerant evaporated in the heat absorber 9 flows out into the refrigerant pipe 13C and merges with the refrigerant from the refrigerant pipe 13D (refrigerant from the outdoor heat exchanger 7), and then sequentially passes through the check valve 40 and the accumulator 12 to the compressor 2. Repeated circulation. Since the air dehumidified by the heat absorber 9 is reheated in the process of passing through the radiator 4, dehumidifying heating in the passenger compartment is thereby performed.

  The controller 32 controls the rotational speed of the compressor 2 based on the target radiator pressure PCO calculated from the target heater temperature TCO and the radiator pressure PCI (high pressure of the refrigerant circuit R) detected by the radiator pressure sensor 47. The valve opening degree of the outdoor expansion valve 6 is controlled based on the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48.

(3) Internal cycle operation Next, the internal cycle operation will be described with reference to FIG. FIG. 5 shows a refrigerant flow (solid arrow) in the refrigerant circuit R in the internal cycle operation. In the internal cycle operation, the controller 32 fully closes the outdoor expansion valve 6 in the dehumidifying and heating operation state (fully closed position). However, the solenoid valve 21 is kept open, and the refrigerant outlet of the outdoor heat exchanger 7 is communicated with the refrigerant suction side of the compressor 2. That is, since this internal cycle operation is a state in which the outdoor expansion valve 6 is fully closed by the control of the outdoor expansion valve 6 in the dehumidifying and heating operation, this internal cycle operation can also be regarded as a part of the dehumidifying and heating operation ( The shutter 23 is open).

  However, since the inflow of the refrigerant to the outdoor heat exchanger 7 is blocked by closing the outdoor expansion valve 6, the condensed refrigerant flowing through the refrigerant pipe 13 </ b> E via the radiator 4 passes through the electromagnetic valve 22 and becomes refrigerant. All flows into the pipe 13F. And the refrigerant | coolant which flows through the refrigerant | coolant piping 13F reaches the indoor expansion valve 8 through the electromagnetic valve 17 from the refrigerant | coolant piping 13B. After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. Since the moisture in the air blown out from the indoor blower 27 by the heat absorption action at this time condenses and adheres to the heat absorber 9, the air is cooled and dehumidified.

  The refrigerant evaporated in the heat absorber 9 flows through the refrigerant pipe 13C, and repeats circulation that is sucked into the compressor 2 through the check valve 40 and the accumulator 12 in order. Since the air dehumidified by the heat absorber 9 is reheated in the process of passing through the radiator 4, dehumidifying heating in the passenger compartment is thereby performed. Since the refrigerant is circulated between the radiator 4 (radiation) and the heat absorber 9 (heat absorption) in the passage 3, heat from the outside air is not pumped up, and heating for the consumed power of the compressor 2 is performed. Ability is demonstrated. Since the entire amount of the refrigerant flows through the heat absorber 9 that exhibits the dehumidifying action, the dehumidifying capacity is higher than the dehumidifying and heating operation, but the heating capacity is lowered.

  Although the outdoor expansion valve 6 is closed, the electromagnetic valve 21 is open, and the refrigerant outlet of the outdoor heat exchanger 7 communicates with the refrigerant suction side of the compressor 2, so that the liquid in the outdoor heat exchanger 7 is The refrigerant flows out through the refrigerant pipe 13D and the electromagnetic valve 21 to the refrigerant pipe 13C, is collected by the accumulator 12, and the outdoor heat exchanger 7 is in a gas refrigerant state. Thereby, compared with when the solenoid valve 21 is closed, the amount of refrigerant circulating in the refrigerant circuit R increases, and the heating capacity in the radiator 4 and the dehumidifying capacity in the heat absorber 9 can be improved.

  The controller 32 controls the rotation speed of the compressor 2 based on the temperature of the heat absorber 9 or the above-described radiator pressure PCI (high pressure of the refrigerant circuit R). At this time, the controller 32 controls the compressor 2 by selecting the lower one of the compressor target rotational speeds obtained from either calculation, depending on the temperature of the heat absorber 9 or the radiator pressure PCI.

(4) Dehumidifying and Cooling Operation Next, the dehumidifying and cooling operation will be described with reference to FIG. FIG. 6 shows a refrigerant flow (solid arrow) in the refrigerant circuit R in the dehumidifying and cooling operation. In the dehumidifying and cooling operation, the controller 32 opens the electromagnetic valve 17 and closes the electromagnetic valve 21. Further, the electromagnetic valve 22 and the electromagnetic valve 20 are closed. And the compressor 2 and each air blower 15 and 27 are drive | operated, and the air mix damper 28 sets it as the state which adjusts the ratio by which the air blown out from the indoor air blower 27 is ventilated by the heat radiator 4. FIG. Further, the shutter 23 is opened. Thereby, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4. Since the air in the air flow passage 3 is passed through the radiator 4, the air in the air flow passage 3 is heated by the high-temperature refrigerant in the radiator 4, while the refrigerant in the radiator 4 heats the air. It is deprived and cooled, and condensates.

  The refrigerant that has exited the radiator 4 reaches the outdoor expansion valve 6 through the refrigerant pipe 13E, and flows into the outdoor heat exchanger 7 through the outdoor expansion valve 6 that is controlled to open. The refrigerant flowing into the outdoor heat exchanger 7 is cooled and condensed by running there or by the outside air ventilated by the outdoor blower 15. The refrigerant exiting the outdoor heat exchanger 7 enters the refrigerant pipe 13B through the refrigerant pipe 13A and the check valve 18, and further reaches the indoor expansion valve 8 through the electromagnetic valve 17. After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. Since the moisture in the air blown out from the indoor blower 27 by the heat absorption action at this time condenses and adheres to the heat absorber 9, the air is cooled and dehumidified.

  The refrigerant evaporated in the heat absorber 9 passes through the check pipe 40 through the refrigerant pipe 13 </ b> C, reaches the accumulator 12, and repeats circulation that is sucked into the compressor 2 through the accumulator 12. Air that has been cooled and dehumidified by the heat absorber 9 is reheated in the process of passing through the radiator 4 (reheating: lower heat dissipation capacity than during heating), so that dehumidification and cooling of the passenger compartment is performed. become.

  The controller 32 sets the heat absorber temperature Te to the target heat absorber temperature TEO based on the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48 and the target heat absorber temperature TEO that is the target value. While controlling the rotation speed of the compressor 2, the target radiator pressure PCO (radiator pressure PCI) calculated from the radiator pressure PCI (high pressure of the refrigerant circuit R) detected by the radiator pressure sensor 47 and the target heater temperature TCO. The required reheat amount by the radiator 4 is obtained by controlling the valve opening degree of the outdoor expansion valve 6 so that the radiator pressure PCI becomes the target radiator pressure PCO.

(5) Cooling Operation Next, the cooling operation will be described with reference to FIG. FIG. 7 shows a refrigerant flow (solid arrow) in the refrigerant circuit R in the cooling operation. In the cooling operation, the controller 32 opens the electromagnetic valve 20 in the dehumidifying and cooling operation state (the valve opening degree of the outdoor expansion valve 6 is free). Note that the air mix damper 28 is in a state of adjusting the ratio of air passing through the radiator 4. Further, the shutter 23 is opened.

  Thereby, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4. Although the air in the air flow passage 3 is ventilated to the radiator 4, the ratio is small (because of only reheating during cooling), so this almost passes through, and the refrigerant exiting the radiator 4 is The refrigerant reaches the outdoor expansion valve 6 through the refrigerant pipe 13E. At this time, since the solenoid valve 20 is opened, the refrigerant passes through the refrigerant pipe 13J through the solenoid valve 20 and flows into the outdoor heat exchanger 7 as it is, and is then circulated by the outdoor air blower 15 by running or by the outdoor blower 15. It is cooled by air and condensed into liquid. The refrigerant exiting the outdoor heat exchanger 7 enters the refrigerant pipe 13B through the refrigerant pipe 13A and the check valve 18, and further reaches the indoor expansion valve 8 through the electromagnetic valve 17. After the refrigerant is depressurized by the indoor expansion valve 8, it flows into the heat absorber 9 and evaporates. Moisture in the air blown out from the indoor blower 27 by the heat absorption action at this time condenses and adheres to the heat absorber 9, and the air is cooled.

  The refrigerant evaporated in the heat absorber 9 goes out to the refrigerant pipe 13C, passes through the check valve 40, reaches the accumulator 12, and repeats circulation sucked into the compressor 2 through the accumulator 12. The air cooled and dehumidified by the heat absorber 9 is blown out from the outlet 29 into the vehicle interior, thereby cooling the vehicle interior. In this cooling operation, the controller 32 controls the rotational speed of the compressor 2 based on the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48.

(6) Switching of air-conditioning operation and control of air mix damper 28 The controller 32 calculates the above-described target blowing temperature TAO from the following equation (I). This target blowing temperature TAO is a target value of the temperature of the air blown out from the blowout port 29 into the vehicle interior.
TAO = (Tset−Tin) × K + Tbal (f (Tset, SUN, Tam))
.. (I)
Here, Tset is the set temperature in the passenger compartment set by the air conditioning operation unit 53, Tin is the temperature of the passenger compartment air detected by the inside air temperature sensor 37, K is a coefficient, Tbal is the set temperature Tset, and the solar radiation sensor 51 detects This is a balance value calculated from the amount of solar radiation SUN to be performed and the outside air temperature Tam detected by the outside air temperature sensor 33. And generally this target blowing temperature TAO is so high that the outside temperature Tam is low, and it falls as the outside temperature Tam rises.

  The controller 32 selects one of the above air conditioning operations based on the outside air temperature Tam detected by the outside air temperature sensor 33 and the target outlet temperature TAO at the time of activation. In addition, after the activation, the air conditioning operations are selected and switched in accordance with changes in the environment and setting conditions such as the outside air temperature Tam and the target blowing temperature TAO.

  In addition, the controller 32 controls the air mix damper 28 with the air volume ratio SW obtained by the equation SW = (TAO−Te) / (TH−Te). This air volume ratio SW is the ratio of air passing through the heat absorber 9 to the heat radiator 4 and varies between 0 (not passing through the heat radiator 4) and 1 (all air passing through the heat radiator 4). To do.

TH for calculating the air volume ratio SW of the air mix damper 28 is the temperature (heating temperature) of the air on the lee side of the radiator 4 described above, and is estimated by the controller 32 from the first-order lag calculation formula (II) shown below. To do.
TH = (INTL × TH0 + Tau × THz) / (Tau + INTL) (II)
Here, INTL is the calculation cycle (constant), Tau is the time constant of the primary delay, TH0 is the steady value of the heating temperature TH in the steady state before the primary delay calculation, and THz is the previous value of the heating temperature TH. By estimating the heating temperature TH in this way, there is no need to provide a special temperature sensor. Note that the controller 32 changes the time constant Tau and the steady value TH0 according to the above-described operation mode, thereby changing the above-described estimation formula (II) depending on the operation mode, and estimates the heating temperature TH.

(7) Temperature Adjustment of Battery 55 Next, temperature adjustment control of the battery 55 by the controller 32 will be described with reference to FIGS. As described above, when the battery 55 is charged and discharged in a state where the temperature is increased due to self-heating or the like, the deterioration proceeds. Therefore, the controller 32 of the vehicle air conditioner 1 of the embodiment cools the temperature of the battery 55 within the appropriate temperature range by the heating device temperature adjustment device 61 while performing the air conditioning operation as described above. Since the appropriate temperature range of the battery 55 is generally set to + 25 ° C. or higher and + 45 ° C. or lower, in the embodiment, the target battery temperature TBO (the target value of the temperature of the battery 55 (battery temperature Tb) is within the appropriate temperature range. For example, + 35 ° C.) is set.

(7-1) First heat medium heat absorption / heating mode (heat medium heat absorption / heating mode)
In the heating operation (FIG. 3), the controller 32 uses, for example, the following formulas (III) and (IV), the target heating capacity TGQhp that is the heating capacity required for the radiator 4 and the radiator 4 The possible heating capacity Qhp is calculated.
TGQhp = (TCO−Te) × Cpa × ρ × Qair (III)
Qhp = f (Tam, NC, BLV, VSP, FANVout, Te) (IV)
Here, Te is the temperature of the heat absorber 9 detected by the heat absorber temperature sensor 48, Cpa is the specific heat [kj / kg · K] of the air flowing into the radiator 4, and ρ is the density of the air flowing into the radiator 4 ( Specific volume) [kg / m ³ ], Qair is the air flow [m ³ / h] passing through the radiator 4 (estimated from the blower voltage BLV of the indoor fan 27), VSP is the vehicle speed obtained from the vehicle speed sensor 52, and FANVout is This is the voltage of the outdoor blower 15.

Further, the controller 32 requests the heat generating device temperature adjustment device 61 using, for example, the following equation (V) based on the temperature of the battery 55 (battery temperature Tb) detected by the battery temperature sensor 76 and the target battery temperature TBO described above. The required battery cooling capacity Qbat, which is the cooling capacity of the battery 55, is calculated.
Qbat = (Tb−TBO) × k1 × k2 (V)
Here, k1 is the specific heat [kj / kg · K] of the heat medium circulating in the heat generating device temperature adjusting device 61, and k2 is the flow rate [m ³ / h] of the heat medium. The formula for calculating the required battery cooling capacity Qbat is not limited to the above, and may be calculated in consideration of other factors related to battery cooling other than the above.

  When the battery temperature Tb is lower than the target battery temperature TBO (Tb <TBO), the required battery cooling capacity Qbat calculated by the above equation (V) is negative, so in the embodiment, the controller 32 sets all the auxiliary expansion valves 73. The heating device temperature adjustment device 61 is also stopped and closed. On the other hand, when the battery temperature Tb rises due to charging / discharging or the like during the heating operation and becomes higher than the target battery temperature TBO (TBO <Tb), the required battery cooling capacity Qbat calculated by the equation (V) is positive. Therefore, in the embodiment, the controller 32 opens the auxiliary expansion valve 73, operates the heat generating device temperature adjusting device 61, and starts cooling the battery 55.

  In that case, the controller 32 compares the two based on the target heating capacity TGQhp and the required battery cooling capacity Qbat, and in the embodiment, the first heat medium heat absorption / heating mode described here and the second heat described later are used. The medium heat absorption / heating mode (both heat medium heat absorption / heating mode in the present invention) is switched and executed.

  First, when the heating load in the passenger compartment is large (for example, the temperature of the inside air is low) and the heat generation amount of the battery 55 is small (the cooling load is small), the target heating capacity TGQhp is larger than the required battery cooling capacity Qbat. (TGQhp> Qbat), the controller 32 executes the first heat medium heat absorption / heating mode. FIG. 8 shows the refrigerant flow (solid arrow) in the refrigerant circuit R and the heat medium flow (broken arrow) in the heating device temperature adjustment device 61 in the first heat medium heat absorption / heating mode.

  In the first heat medium absorption / heating mode, the controller 32 further opens the electromagnetic valve 22 and opens the auxiliary expansion valve 73 to control the valve opening degree in the heating operation state of the refrigerant circuit R shown in FIG. State Then, the circulation pump 62 of the heat generating device temperature adjusting device 61 is operated. Thereby, a part of the refrigerant discharged from the radiator 4 is diverted on the refrigerant upstream side of the outdoor expansion valve 6 and reaches the refrigerant upstream side of the electromagnetic valve 17 through the refrigerant pipe 13F. The refrigerant then enters the branch pipe 72 and is depressurized by the auxiliary expansion valve 73, and then flows into the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64 via the branch pipe 72 and evaporates. At this time, an endothermic effect is exhibited. The refrigerant evaporated in the refrigerant flow path 64B is repeatedly circulated through the refrigerant pipe 74, the refrigerant pipe 13C, and the accumulator 12 and then sucked into the compressor 2 (indicated by solid arrows in FIG. 8).

  On the other hand, the heat medium discharged from the circulation pump 62 passes through the heat medium heater 66 to reach the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64 through the heat medium pipe 68, where it evaporates in the refrigerant flow path 64B. The refrigerant absorbs heat and the heat medium is cooled. The heat medium cooled by the endothermic action of the refrigerant exits the refrigerant-heat medium heat exchanger 64 and reaches the battery 55. After cooling the battery 55, the heat medium is repeatedly sucked into the circulation pump 62 (the broken line in FIG. 8). Indicated by an arrow).

  In this way, in the first heat medium heat absorption / heating mode, the refrigerant in the refrigerant circuit R evaporates in the outdoor heat exchanger 7 and the refrigerant-heat medium heat exchanger 64, absorbs heat from the outside air, and generates the temperature of the heating device. 61 also absorbs heat from the heat medium 61 (battery 55). Thus, heat is pumped from the battery 55 via the heat medium, and the pumped heat is conveyed to the radiator 4 while being cooled, and can be used for heating the passenger compartment.

  In the first heat medium heat absorption / heating mode, the target heating capacity TGQhp cannot be achieved by the above-described heating capacity Qhp of the radiator 4 even by heat absorption from the outside air and heat absorption from the battery 55 as described above (TGQhp> Qhp). The controller 32 generates heat (energization) in the heat medium heater 66.

  When the heat medium heater 66 generates heat, the heat medium discharged from the circulation pump 62 of the heat generating device temperature adjustment device 61 is heated by the heat medium heater 66 and then the heat medium flow of the refrigerant-heat medium heat exchanger 64. Since the heat flows into the path 64A, the heat of the heat medium heater 66 is also pumped up by the refrigerant evaporating in the refrigerant flow path 64B, and the heating capacity Qhp by the radiator 4 is increased to achieve the target heating capacity TGQhp. Will be able to. The controller 32 stops the heat generation of the heat medium heater 66 (non-energization) when the heating capacity Qhp can achieve the target heating capacity TGQhp.

(7-2) Second Heat Transfer Absorption / Heating Mode Next, when the heating load in the passenger compartment and the cooling load of the battery 55 are substantially the same, that is, the target heating capacity TGQhp and the required battery cooling capacity Qbat are equal or approximate. If so (TGQhp≈Qbat), the controller 32 executes the second heat medium heat absorption / heating mode. FIG. 9 shows the refrigerant flow (solid arrow) in the refrigerant circuit R and the heat medium flow (broken arrow) in the heating device temperature adjusting device 61 in the second heat medium heat absorption / heating mode.

  In the second heat medium heat absorption / heating mode, the controller 32 closes the electromagnetic valves 17, 20, and 21, fully closes the outdoor expansion valve 6, opens the electromagnetic valve 22, and opens the auxiliary expansion valve 73 to open the valve. The state is controlled. And the compressor 2 and the indoor air blower 27 are drive | operated, and the circulation pump 62 of the heat generating apparatus temperature control apparatus 61 is also drive | operated. Thereby, all the refrigerant | coolants which came out from the heat radiator 4 flow into the solenoid valve 22, and come to the refrigerant | coolant upstream side of the solenoid valve 17 through the refrigerant | coolant piping 13F. The refrigerant then enters the branch pipe 72 and is depressurized by the auxiliary expansion valve 73, and then flows into the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64 via the branch pipe 72 and evaporates. At this time, an endothermic effect is exhibited. The refrigerant evaporated in the refrigerant flow path 64B is repeatedly circulated through the refrigerant pipe 74, the refrigerant pipe 13C, and the accumulator 12 (indicated by solid arrows in FIG. 9).

  On the other hand, the heat medium discharged from the circulation pump 62 passes through the heat medium heater 66 to reach the heat medium flow path 64A of the refrigerant-heat medium heat exchanger 64 through the heat medium pipe 68, where it evaporates in the refrigerant flow path 64B. The refrigerant absorbs heat and the heat medium is cooled. The heat medium cooled by the endothermic action of the refrigerant exits the refrigerant-heat medium heat exchanger 64 and reaches the battery 55, and after the battery 55 is cooled, the circulation sucked into the circulation pump 62 is repeated (the broken line in FIG. 9). Indicated by an arrow).

  In this way, in the second heat medium heat absorption / heating mode, the refrigerant in the refrigerant circuit R evaporates in the refrigerant-heat medium heat exchanger 64 and absorbs heat only from the heat medium (battery 55) of the heating device temperature adjustment device 61. To do. As a result, the refrigerant does not flow into the outdoor heat exchanger 7, and the refrigerant pumps up heat only from the battery 55 via the heat medium, so that while solving the problem of frost formation on the outdoor heat exchanger 7, The battery 55 can be cooled and the heat pumped up from the battery 55 can be transferred to the radiator 4 to heat the passenger compartment.

  In addition, the auxiliary expansion valve 73 is opened and the valve opening degree in the above-described dehumidifying and heating operation (FIG. 4), internal cycle operation (FIG. 5), dehumidifying and cooling operation (FIG. 6), and cooling operation (FIG. 7). And the circulation pump 62 is operated to evaporate the refrigerant in the refrigerant flow path 64B of the refrigerant-heat medium heat exchanger 64 and absorb the heat from the heat medium, thereby cooling the battery 55 and adjusting its temperature. can do.

(8) Control of switching from heating operation to first and second heat medium heat absorption / heating mode when there is a possibility that outside air heat absorption is not possible Next, with reference to FIGS. In 3), switching control from the heating operation to the first and second heat medium heat absorption / heating mode when there is a possibility that the outdoor heat exchanger 7 cannot absorb heat from the outside air (the outside air cannot absorb heat) will be described. .

After starting the heating operation described above in step S1 of FIG. 10, the controller 32 executes step S3 while the heating operation is being executed in step S2, and the outdoor heat exchanger 7 can absorb the refrigerant from the outside air. Judging whether there is a possibility of disappearing. The determination condition in step S3 is referred to as an outside air endothermic prediction determination condition. The outside air endothermic non-prediction prediction determination condition is, for example, any one of (i) to (v) shown below, a combination thereof, or all of them.
(I) The suction refrigerant temperature Ts of the compressor 2 detected by the suction temperature sensor 44 has decreased to a predetermined value Ts1 or less.
(Ii) The amount of frost formation on the outdoor heat exchanger 7 has increased to a predetermined value Fr1 or more.
(Iii) The speed of frost formation on the outdoor heat exchanger 7 has increased to a predetermined value X1 or more.
(Iv) The outside air temperature Tam detected by the outside air temperature sensor 33 has decreased to a predetermined value Tam1 or less.
(V) The decrease rate of the outside air temperature Tam detected by the outside air temperature sensor 33 has increased to a predetermined value Y1 or more.

  In a state where frost has grown on the outdoor heat exchanger 7 or in an environment where the outdoor air temperature Tam decreases, the outdoor heat exchanger 7 may not be able to absorb heat from the outdoor air. In the condition (i), when the outside air temperature Tam decreases or when frost forms on the outdoor heat exchanger 7 and it becomes difficult to absorb heat from the outside air, the suction refrigerant temperature Ts of the compressor 2 decreases. Based on coming. In addition, the amount of frost formation and the frost formation speed under the above conditions (ii) and (iii) are, for example, the outdoor heat exchanger temperature TXO and the outdoor heat exchanger pressure PXO of the outdoor heat exchanger 7 and the outdoor heat exchanger 7. Can be obtained from the difference between these values when there is no frost formation (non-frost outdoor heat exchanger temperature TXObase, non-frost outdoor heat exchanger pressure PXObase, obtained in advance).

  The predetermined values Ts1, Fr1, X1, Tam1, and Y1 are obtained in advance by experiments as values that may cause the outdoor heat exchanger 7 to be unable to absorb heat from the outside air. Then, the controller 32 determines that the outdoor air heat absorption impossibility prediction determination condition is satisfied, and any of the above conditions (i) to (v), a combination thereof, or all of them is satisfied in step S3, and the outdoor heat The exchanger 7 determines that there is a possibility that the refrigerant cannot absorb heat from the outside air, and proceeds to step S4 to first operate the circulation pump 62 of the heat generating device temperature adjusting device 61 to circulate the heat medium through the heat medium pipe 68.

  Next, based on the output of the heat medium temperature sensor 80, the controller 32 determines whether or not the temperature of the heat medium exiting the heat medium heater 66 (heat medium temperature Tw) is equal to or lower than a predetermined threshold T1 in step S5. To do. In this case, the controller 32 holds the heat medium temperature MAP that can be transferred to the heat medium endotherm shown in FIG. The heat medium temperature MAP that can be transferred to the heat medium endotherm indicates a relationship between the above-described target heating capacity TGQhp and the threshold value T1 that is the heat medium temperature Tw that cannot achieve the target heating capacity TGQhp. As the heating capacity TGQhp increases, the threshold T1 also increases.

  In addition to the target heating capacity TGQhp, any one of the above-described target blowing temperature TAO, the blower voltage BLV of the indoor blower 27, the above-described target heater temperature TCO, or a combination of these and the target heating capacity TGQhp, Or you may determine threshold value T1 based on all of these.

  In step S5, the controller 32 determines a threshold value T1 from the heat medium temperature MAP that can be transferred to the heat medium endotherm and the target heating capacity TGQhp at that time, and determines whether the heat medium temperature Tw is equal to or lower than the threshold value T1. When the heat medium temperature Tw is low and is equal to or less than the threshold value T1, the controller 32 determines that the vehicle interior cannot be heated by absorbing heat from the heat medium, and proceeds from step S5 to step S9 to perform the heat medium preheating operation. To start.

  In this heat medium preheating operation, the controller 32 energizes the heat medium heater 66 to generate heat. As a result, the heat medium circulated by the circulation pump 62 is heated by the heat medium heater 66, so that the heat medium temperature Tw increases. When the heat medium temperature Tw becomes higher than the threshold value T1 (may be a value (T1 + α1) having a predetermined hysteresis α1), the controller 32 proceeds to step S6.

In step S <b> 6, the controller 32 determines whether or not the outdoor heat exchanger 7 can still absorb heat from the outside air. The determination condition in step S6 is referred to as an outdoor air heat absorption possible determination condition. The determination condition for the ability to absorb heat from the outside air is, for example, any one of (vi) to (x) shown below, a combination thereof, or all of them.
(Vi) The suction refrigerant temperature Ts of the compressor 2 detected by the suction temperature sensor 44 is equal to or higher than a predetermined value Ts2 lower than the predetermined value Ts1.
(Vii) The amount of frost formation on the outdoor heat exchanger 7 is equal to or less than a predetermined value Fr2 greater than the predetermined value Fr1.
(Viii) The progress speed of frost formation on the outdoor heat exchanger 7 is equal to or less than a predetermined value X2 that is faster than the predetermined value X1.
(Ix) The outside air temperature Tam detected by the outside air temperature sensor 33 is not less than a predetermined value Tam2 lower than the predetermined value Tam1.
(X) The decrease rate of the outside air temperature Tam detected by the outside air temperature sensor 33 is equal to or less than a predetermined value Y2 that is faster than the predetermined value Y1.

  The predetermined values Ts2, Fr2, X2, Tam2, and Y2 are obtained in advance by experiments as values that can still absorb heat from the outside air in the outdoor heat exchanger 7. Then, if any of the above conditions (vi) to (x), or a combination thereof, or all of them are satisfied in step S6, the controller 32 determines that the outdoor air heat absorption possibility determination condition is satisfied, and the outdoor heat is still The exchanger 7 determines that the refrigerant can absorb heat from the outside air, and proceeds to step S7 to execute the first heat medium heat absorption / heating mode (FIG. 8) described above (first heat medium heat absorption / Switch to heating mode).

  In the first heat-medium heat absorption / heating mode, as described above, the refrigerant in the refrigerant circuit R evaporates in the outdoor heat exchanger 7 and the refrigerant-heat medium heat exchanger 64, absorbs heat from the outside air, and generates the temperature of the heating device. 61 also absorbs heat from the heat medium 61, pumps heat from the battery 55 and the heat medium heater 66 (when energized) via the heat medium, conveys the pumped heat to the radiator 4, and It can be used for room heating.

  On the other hand, if the outdoor air heat absorption possibility determination condition is not satisfied in step S6, it is determined that heat cannot be absorbed from the outdoor air in the outdoor heat exchanger 7, and the process proceeds to step S8 where the second heat medium heat absorption / heating described above is performed. The mode (FIG. 9) is executed (switching to the second heat medium heat absorption / heating mode). Further, the heat medium heater 66 generates heat as necessary. Thereby, the heat pumped up from the battery 55 and the heat medium heater 66 can be conveyed to the radiator 4 to heat the passenger compartment.

  Here, FIG. 12 shows changes in the target blowing temperature TAO, the heating temperature TH, and the heat medium temperature Tw when the heating operation is shifted to the second heat medium heat absorption / heating mode. NC is the rotation speed of the compressor 2, L1 is the amount of frost formation of the outdoor heat exchanger 7, and L2 is the maximum value MAXNC of the rotation speed NC of the compressor 2. In FIG. 12, time t1 indicates the time when the heat medium preheating operation is started in step S9 of FIG. 10, and t2 indicates the time when the second heat medium heat absorption / heating mode is started in step S8.

  When the heat medium temperature Tw is low (for example, 0 ° C. or less, which is equal to or less than the threshold value T1 described above) and the heat medium preheating operation is not performed as in step S9 of the embodiment, the heat medium temperature Tw is a broken line in FIG. Therefore, the discharge pressure of the compressor 2 becomes low as indicated by P1 in the ph diagram of FIG. 14, and the second heat medium endotherm is absorbed at time t2. / Even when the heating mode is started, the heating temperature TH temporarily decreases as indicated by the broken line in FIG. 12 (the rotational speed NC of the compressor 2 also decreases). As a result, the passenger feels uncomfortable.

  On the other hand, when the heat medium preheating operation is executed in step S9 before switching from the heating operation to the second heat medium absorption / heating mode as in the present invention, the heat medium temperature Tw increases from time t1, and at time t2. Since it is higher than the threshold value T1 (for example, + 20 ° C.), the discharge pressure of the compressor 2 becomes higher as indicated by P2 in the ph diagram of FIG. 13, and the second heat medium endotherm / By starting the heating mode, the heating temperature TH increases without greatly decreasing from the target blowing temperature TAO as shown by the solid line in FIG. 12 (the rotational speed NC of the compressor 2 also increases).

  As described above in detail, the present invention includes a battery 55 (a heat generating device temperature adjusting device 61 for adjusting the temperature of the battery 55 by circulating a heat medium in the heat generating device and mounted on the vehicle. The apparatus 61 includes a heat medium heater 66 for heating the heat medium, and a refrigerant-heat medium heat exchanger 64 for exchanging heat between the refrigerant and the heat medium, and the controller 32 discharges from the compressor 2. The first and second heat-medium heat absorption / heating modes in which heat is absorbed by the refrigerant-heat medium heat exchanger 64 after the discharged refrigerant is radiated by the radiator 4 and the radiated refrigerant is decompressed. Therefore, if the first and second heat medium heat absorption / heating modes are switched, the vehicle interior is efficiently heated by absorbing heat from the heat medium of the heat generating device temperature adjusting device 61, for example, being attached to the outdoor heat exchanger 7. Appropriate while suppressing frost Even when the battery 55 is cooled or the outdoor heat exchanger 7 is frosted and cannot absorb heat from the outside air, the vehicle interior can be heated by absorbing heat from the heat medium of the heating device temperature adjusting device 61. It becomes like this.

  In particular, when the controller 32 switches from the heating operation to the first and second heat medium heat absorption / heating modes, if the heat medium temperature Tw is equal to or less than a predetermined threshold value T1, the first and second heat medium heat absorption / heating are performed. Before switching to the mode, the heating medium is heated by the heating medium heater 66 and the temperature of the heating medium is increased, and then the first and second heating medium heat absorption / heating modes are switched. Thus, sufficient heating capacity can be secured when switching from the first to the second heat medium heat absorption / heating mode. As a result, the temperature of the heat medium is switched to the first and second heat medium heat absorption / heating modes in a state where the temperature of the heat medium is low, and the temperature of the air blown into the vehicle interior from the air outlet 29 (blowout temperature; matches the heating temperature TH). ) Temporarily decreases, and the inconvenience that the passenger feels uncomfortable or uncomfortable can be solved.

  In the embodiment, the controller 32 determines that the outdoor heat exchanger 7 may not be able to absorb heat from the outside air when the predetermined outside air heat absorption impossibility prediction determination condition is satisfied in the heating operation, and the temperature of the heat medium is the threshold value T1. It is determined whether the temperature is equal to or less than the threshold value T1, and heating of the heat medium by the heat medium heater 66 is started, and the temperature of the heat medium is at least higher than the threshold value T1 (is higher than the threshold value T1, Waiting for the temperature to rise to a temperature higher than T1 + α1), the first and second heat medium heat absorption / heating modes are shifted to the first and second heat medium heat absorption / heating modes. Switching can be performed smoothly.

  The outside air heat absorption impossibility prediction determination condition is that the suction refrigerant temperature Ts of the compressor 2 is lowered to a predetermined value Ts1 or less as in the embodiment, and the frost formation amount to the outdoor heat exchanger 7 is increased to a predetermined value Fr1 or more. The progress of frost formation on the outdoor heat exchanger 7 has increased to a predetermined value X1 or higher, the outdoor air temperature Tam has decreased to a predetermined value Tam1 or lower, and the lowering speed of the outdoor air temperature Tam has increased to a predetermined value Y1 or higher. Preferably, at least one of the above is included.

  In the embodiment, the controller 32 has a target heating capacity TGQhp of the radiator 4, a target blowing temperature TAO that is a target value of the air temperature blown into the vehicle interior, and a blower voltage BLV of the indoor blower 27 that passes through the air flow passage 3. Since the threshold value T1 is determined based on at least one of the target heater temperature TCO, which is the target value of the air temperature (heating temperature TH) on the lee side of the radiator 4, the heat medium heater It is possible to appropriately determine whether or not the heat medium needs to be heated by 66, and to avoid unnecessary heating by the heat medium heater 66.

  In the embodiment, the controller 32 determines that the outdoor heat exchanger 7 can absorb heat from the outside air when a predetermined outdoor air heat absorption possibility determination condition is satisfied, and the refrigerant radiated by the radiator 4 is used as the outdoor heat exchanger. 7 and the first heat-medium heat absorption / heating mode in which heat is absorbed by the refrigerant-heat medium heat exchanger 64, the heat exchange from the heat medium is possible when the outdoor heat exchanger 7 can absorb heat from the outside air. In addition to the heat absorption, heat is also absorbed from the outside air, and the vehicle interior can be heated.

  As conditions for determining whether the outside air can absorb heat, the suction refrigerant temperature Ts of the compressor 2 is equal to or higher than a predetermined value Ts2 lower than the predetermined value Ts1, as in the embodiment, and the amount of frost formation on the outdoor heat exchanger 7 is based on the predetermined value Fr1. It is not more than the predetermined value Fr2, the frosting speed to the outdoor heat exchanger 7 is not more than the predetermined value X2 that is faster than the predetermined value X1, and the outside air temperature Tam is not less than the predetermined value Tam2 that is lower than the predetermined value Tam1. It is preferable that the rate of decrease in the outside air temperature Tam is at least one of the predetermined value Y2 that is faster than the predetermined value Y1.

  It should be noted that the configurations of the refrigerant circuit R and the heat-generating equipment temperature adjusting device 61 described in the above embodiments are not limited thereto, and needless to say, can be changed without departing from the spirit of the present invention.

DESCRIPTION OF SYMBOLS 1 Vehicle air conditioner 2 Compressor 3 Air flow path 4 Radiator 6 Outdoor expansion valve 7 Outdoor heat exchanger 8 Indoor expansion valve 9 Heat absorber 17, 20, 21, 22 Solenoid valve 27 Indoor blower 28 Air mix damper 32 Controller (Control device)
55 Battery (heat generating device)
61 Heating device temperature control device 62 Circulating pump 64 Refrigerant-heat medium heat exchanger 66 Heat medium heater (heating device)
72 Branch piping (branch circuit)
73 Auxiliary expansion valve 80 Heat medium temperature sensor R Refrigerant circuit

Claims (6)

A compressor for compressing the refrigerant;
An air flow passage through which air to be supplied into the passenger compartment flows;
A radiator for dissipating the refrigerant and heating the air supplied from the air flow passage to the vehicle interior;
An outdoor heat exchanger provided outside the passenger compartment for absorbing the refrigerant;
Equipped with a control device,
Vehicle air for performing a heating operation in which at least the refrigerant discharged from the compressor is radiated by the radiator and the radiated refrigerant is decompressed by the control device, and then the heat is absorbed by the outdoor heat exchanger. In the harmony device,
A heating device temperature adjusting device for adjusting the temperature of the heating device by circulating a heat medium to the heating device mounted on the vehicle,
The heating device temperature adjustment device has a heating device for heating the heat medium, and a refrigerant-heat medium heat exchanger for exchanging heat between the refrigerant and the heat medium,
The control device radiates the refrigerant discharged from the compressor with the radiator, depressurizes the radiated refrigerant, and then absorbs heat with the refrigerant-heat medium heat exchanger. Have
When switching from the heating operation to the heat medium heat absorption / heating mode, if the temperature of the heat medium is equal to or lower than a predetermined threshold T1, the heat medium is switched by the heating device before switching to the heat medium heat absorption / heating mode. The vehicle air conditioner is switched to the heat medium heat absorption / heating mode after heating and raising the temperature of the heat medium.   The control device determines that the outdoor heat exchanger may not be able to absorb heat from outside air when a predetermined outside air heat absorption impossibility prediction determination condition is satisfied in the heating operation, and the temperature of the heat medium is equal to or less than the threshold value T1. If it is equal to or less than the threshold value T1, the heating device starts heating the heating medium, and waits for the temperature of the heating medium to rise to at least a temperature higher than the threshold value T1. The vehicle air conditioner according to claim 1, wherein the vehicle air conditioner shifts to a heat medium heat absorption / heating mode.   The outside air heat absorption impossibility prediction determination condition is that the suction refrigerant temperature Ts of the compressor has decreased to a predetermined value Ts1 or less, the amount of frost formation on the outdoor heat exchanger has increased to a predetermined value Fr1 or more, and the outdoor heat Among the fact that the progress speed of frost formation on the exchanger has increased to a predetermined value X1 or higher, the outside air temperature Tam has decreased to a predetermined value Tam1 or lower, and the lowering speed of the outside air temperature Tam has increased to a predetermined value Y1 or higher. The vehicle air conditioner according to claim 2, comprising at least one of the following.   The control device includes a target heating capacity TGQhp of the radiator, a target blowing temperature TAO which is a target value of the air temperature blown into the vehicle interior, a voltage BLV of the indoor blower passing through the air flow passage, 4. The threshold value T <b> 1 is determined based on at least one of a target heater temperature TCO that is a target value of air temperature on the leeward side. 5. Air conditioner for vehicles.   When executing the heat medium heat absorption / heating mode, the control device determines that the outdoor heat exchanger can absorb heat from the outside air when the predetermined outdoor air heat absorption possibility determination condition is satisfied, and the heat radiator The vehicle air conditioner according to any one of claims 1 to 4, wherein the radiated refrigerant absorbs heat by the outdoor heat exchanger and the refrigerant-heat medium heat exchanger.   The outside air heat absorption possibility determination condition is that the suction refrigerant temperature Ts of the compressor is equal to or higher than a predetermined value Ts2 lower than the predetermined value Ts1, and a frosting amount on the outdoor heat exchanger is higher than the predetermined value Fr1. It is Fr2 or less, the frosting speed to the outdoor heat exchanger is not more than a predetermined value X2 that is faster than the predetermined value X1, and the outside air temperature Tam is not less than a predetermined value Tam2 that is lower than the predetermined value Tam1. 6. The vehicle air conditioner according to claim 5, comprising at least one of a lowering speed of the outside air temperature Tam being equal to or lower than a predetermined value Y <b> 2 that is faster than the predetermined value Y <b> 1.

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